CN106062363A - Sealed compressor and refrigeration device - Google Patents
Sealed compressor and refrigeration device Download PDFInfo
- Publication number
- CN106062363A CN106062363A CN201580010415.XA CN201580010415A CN106062363A CN 106062363 A CN106062363 A CN 106062363A CN 201580010415 A CN201580010415 A CN 201580010415A CN 106062363 A CN106062363 A CN 106062363A
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- China
- Prior art keywords
- piston
- cylinder
- type compressor
- hermetic type
- sliding surface
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
- F04B39/0022—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons piston rods
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/02—Compressor arrangements of motor-compressor units
- F25B31/023—Compressor arrangements of motor-compressor units with compressor of reciprocating-piston type
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Compressor (AREA)
Abstract
The present invention provides a highly efficient sealed compressor which reduces wrenching that occurs due to the incline of a piston during an intake stroke. A compression element of the compressor is provided with a shaft (110) having an eccentric shaft part integrally interlocked with a main shaft part, and a bearing part (120) axially supporting the shaft; an angle (a1) formed by a first center line (141) indicating the axial center of the bearing part and a second center line (142) indicating the axial center (D) of a cylinder (115), and the absolute value (c1) of the angle of inclination of the shaft relative to the bearing part, satisfy equation (1); and provided in the outer peripheral surface of a piston (123) are a seal part (123a) forming a sliding surface, an extending part (123b) forming a sliding surface positioned to the rear of the seal part, and a non-sliding part (123c) that does not form a sliding surface. a1 = n/2 + c1....... (1)
Description
Technical field
The present invention relates to reduce the hermetic type compressor of the slippage loss of piston and be mounted with the system of this hermetic type compressor
Device for cooling.
Background technology
In recent years, about the hermetic type compressor used in the refrigerating plants such as freezer, in order to reduce consumption electric power, phase
Hope further high efficiency.
In such a case, in this hermetic type compressor, pass through reduction reciprocating in discharge chambe
Jam (こ じ り) during the compression travel of piston, thus reduce slippage loss, improve efficiency (for example, referring to patent documentation 1).
Hereinafter, referring to the drawings existing hermetic type compressor is illustrated.Fig. 8 is the vertical of existing hermetic type compressor
Sectional view.Fig. 9 is the main portion sectional view of the piston periphery in the compression travel of existing hermetic type compressor.Figure 10 is
The main portion sectional view of the piston periphery in the suction stroke of existing hermetic type compressor.
In figs. 8 to 10, it is accommodated with in the hermetic container 301 of existing hermetic type compressor there is stator 302 He
The electrical components 304 of rotor 303 and the compression element 305 driven by this electrical components 304.Rotary shaft 310 has main shaft part
311 and eccentric axial portion 312 that is eccentric in its one end and that formed.Rotor 303 is fixed on main shaft part 311.
Cylinder body 314 has cylinder 315 and the bearing portion 320 of general cylindrical shape.Piston freely reciprocally it is fitted with in cylinder 315
323, at its end face, valve plate 350 is installed.Discharge chambe 316 is formed by cylinder 315 and piston 323.
In piston 323, as it is shown in figure 9, be provided with piston pin 325 in the way of parallel with eccentric axial portion 312.Bearing portion
320 form cantilever bearings by the main shaft part 311 of axle supporting rotating shaft 310.
Connecting rod 326 is made up of big bore ends 328, aperture end 329 and bar portion 330.Big bore ends 328 is flush-mounted in eccentric shaft
Portion 312.Aperture end 329 links with piston 323 via piston pin 325.Connecting rod 326 and piston pin 325 is utilized to link eccentric shaft
Portion 312 and piston 323.
It addition, in the drawings, axle center C represents that the axle center of piston 323, axle center D represent the axle center of cylinder 315.
About existing hermetic type compressor configured as described above, below its action is illustrated.Electrical components 304
During energising, rotor 303 makes rotary shaft 310 rotate.The rotation of accompanying rotation axle 310, via connecting rod 326 by eccentric axial portion 312
Piston 323 is passed in rotary motion.Thus, piston 323 moves back and forth in cylinder 315.By the reciprocating motion of piston 323, from tool
The cooling system (not shown) having kind of refrigeration cycle sucks refrigerant gas in discharge chambe 316.Refrigerant gas is at discharge chambe 316
Interior compressed after, then be discharged in cooling system.
In the reciprocating compression travel of piston 323, due to compressive load that refrigerant gas is compressed and
Piston 323 is pressed to eccentric axial portion 312 side, so rotary shaft 310 is tilted at bearing portion 320.Along with this rotary shaft 310
Tilting, the axle center C of piston 323 also tilts.Therefore, in order to the axle center D of the axle center C and cylinder 315 that make piston 323 is when compression travel
Unanimously, the axle center D of cylinder 315 is formed obliquely.Thereby, it is possible to the jam of the piston 323 alleviated in compression travel in cylinder 315,
Reduce slippage loss, it is achieved high efficiency.
But, in existing hermetic type compressor, as shown in Figure 10, at the reciprocating suction stroke of piston 323
In, the attraction load sucking refrigerant gas piston 323 is pulled to cylinder 315 side, so rotary shaft 310 rolls tiltedly to cylinder 315.
Therewith, the axle center D of the cylinder 315 formed relative to tilting in advance, the axle center C of piston 323 there occurs skew.In particular, exist
Under the operating condition that compression ratio is high and strict etc., when attracting load to increase, in order to the leading section of piston 323 is urged to discharge chambe
The bottom surface side of 316, the axle center C of piston 323 can more tilt.Therefore, have and occur jam and input to increase so in piston 323
Problem.
Prior art literature
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Application Publication 2011-508840 publication
Summary of the invention
The present invention is to solve the invention of such existing problem, and its offer can alleviate when suction stroke because piston inclines
The jam tiltedly occurred, the increase preventing input, hermetic type compressor that efficiency is high.
The hermetic type compressor of the present invention is accommodated with electrical components in hermetic container and utilizes electrical components to drive
The hermetic type compressor of compression element.Compression element includes: have main shaft part and the eccentric axial portion with main shaft part one motion
Rotary shaft；The bearing portion of cantilever bearings is formed with the main shaft part by axle supporting rotating shaft.It addition, compression element includes: right
The cylinder that gas is compressed；Can reciprocally be inserted into the piston of the inside of cylinder；With the company linking eccentric axial portion and piston
Bar.It addition, represent the 1st centrage in the axle center of bearing portion and the 2nd centrage angulation a1 in the axle center of expression cylinder and rotation
Rotating shaft meets formula (1) relative to the absolute value c1 at the angle of inclination of bearing portion.It addition, the outer peripheral face at piston is provided with and cylinder
Inner peripheral surface there is gap, form the sealing of sliding surface；It is positioned at the rear of sealing, forms the extension of sliding surface；And position
In the rear of sealing, it is formed without the non-slip portion of sliding surface.
A1=pi/2+c1 ... (1)
Thus, when suction stroke, even if in the case of the axle center skew in the axle center of cylinder with the axle center of piston becomes greatly,
Form the rear of the sealing of the sliding surface of piston, there is also the lateral prolongation forming sliding surface.Thus, at vertical upper and lower
The most there is not the part becoming sliding surface.Therefore, it is possible to the card of the local on vertical above-below direction when alleviating tilting of the piston
Resistance.
The hermetic type compressor of the present invention can alleviate the jam of the local in the suction stroke of piston, prevents input
Increase, it is possible to improve efficiency.
Accompanying drawing explanation
Fig. 1 is the longitudinal section of the hermetic type compressor of embodiments of the present invention 1.
When Fig. 2 is that compressive load works when the compression travel of the hermetic type compressor of embodiments of the present invention 1
Major part amplification sectional view.
When Fig. 3 is to attract load to work when the suction stroke of the hermetic type compressor of embodiments of the present invention 1
Major part amplification sectional view.
Fig. 4 is the cross-sectional top view of the cylinder of the hermetic type compressor of embodiments of the present invention 1, piston.
Fig. 5 is the longitudinal section of the cylinder of the hermetic type compressor of embodiments of the present invention 1, piston.
Fig. 6 is the main of bearing portion and the position relationship of cylinder of the hermetic type compressor representing embodiments of the present invention 1
Partial section view.
Fig. 7 is the summary sectional view of the freezer in embodiments of the present invention 2.
Fig. 8 is the longitudinal section of existing hermetic type compressor.
Fig. 9 is the main portion sectional view of the piston periphery in the compression travel of existing hermetic type compressor.
Figure 10 is the main portion sectional view of the piston periphery in the suction stroke of existing hermetic type compressor.
Detailed description of the invention
Hereinafter, referring to the drawings embodiments of the present invention are illustrated.Additionally, the present invention is not limited by these embodiments
Fixed.
(embodiment 1)
Fig. 1 is the longitudinal section of the hermetic type compressor of embodiments of the present invention 1.Fig. 2 is at this hermetic type compressor
Compression travel time compressive load major part amplification sectional view when working.Fig. 3 is the suction at this hermetic type compressor
Major part amplification sectional view when attracting load to work during stroke.Fig. 4 is the top view of the cylinder of this hermetic type compressor, piston
Sectional view.Fig. 5 is the longitudinal section of the cylinder of this hermetic type compressor, piston.Fig. 6 is the bearing portion representing this hermetic type compressor
Main portion sectional view with the position relationship of cylinder.
In Fig. 1～Fig. 6, be accommodated with in hermetic container 101 electrical components 104 with stator 102 and rotor 103 with
And the compression element 105 driven by this electrical components 104.It addition, the bottom in hermetic container 101 is stored with lubricating oil 106.
It addition, be full of the cold-producing medium 106 of the R600a of hydro carbons in hermetic container 101, enclose VG3's～VG10 in bottom
The lubricating oil 102 of light viscosity oil.
Electrical components 104 is made up of rotor 103 and stator 102, utilizes inverter (not shown) with including at least power supply frequency
Multiple operating frequencys of operating frequency more than rate are driven.The highest operating frequency driving electrical components 104 is 80Hz, with
The operating frequency of minimum more than operating frequency 17Hz drives.
Rotary shaft 110 has main shaft part 111 and to the one of main shaft part 111 in the way of moving with this main shaft part 111 one
The eccentric axial portion 112 that end is eccentric and is formed.Rotor 103 is fixed on main shaft part 111.Set in the inside of rotary shaft 110 and/or surface
It is equipped with fuel feeding path 113.The bottom of fuel feeding path 113 extends to the rule of lubricating oil 106 in the way of being immersed in lubricating oil 106
The position of depthkeeping degree.
Cylinder body 114 has cylinder 115 and the bearing portion 120 of cylindrical shape (also including substantially cylindrical shape).Bearing portion 120 passes through
The main shaft part 111 of axle supporting rotating shaft 110 and form cantilever bearings.
Piston 123 is freely reciprocally inserted in cylinder 115.Valve plate 150 is installed on the end of cylinder 115.By cylinder 115 and piston
123 form discharge chambe 116.
In the way of parallel with eccentric axial portion 112, piston pin 125 is installed on piston 123.As shown in Figure 4 and Figure 5, exist
The outer peripheral face of piston 123 is provided with sealing 123a and extension 123b.Sealing 123a deposits with the inner peripheral surface relative to cylinder 115
Sliding surface is formed on the mode cylindrical shape ground of little clearance (clearance).Extension 123b is than sealing 123a rearward
Two sides there is the radius identical with sealing 123a, the axle at piston 123 be upwardly formed with one fixed width extend slip
Face.Than sealing 123a vertical top and bottom rearward, relative to the inner peripheral surface of cylinder 115, there is bigger clearance, thus set
Put skid-resistant non-slip portion 123c.
As in figure 2 it is shown, connecting rod 126 is made up of big bore ends 128, aperture end 129 and bar portion 130.Big bore ends 128 is embedding
It is contained in eccentric axial portion 112.Aperture end 129 links with piston 123 via piston pin 125.Utilize connecting rod 126 and piston pin
125 link eccentric axial portion 112 and piston 123.
Wherein, it is however generally that, constitute the rotary shaft 110 of a part of compression element 105, connecting rod 126, piston pin 125 and
Piston 123, with the axle center 144 of the main shaft part 111 of rotary shaft 110 and the axle center C of reciprocating piston 123 for angle pi/2
(rad) mode is assembled together.This is because drive loss to diminish when the most smooth during operating.This embodiment party
The structure of formula is formed the most in such a way.
It addition, about the size of the piston 123 in present embodiment, a diameter of 26mm, total length is 23mm, sealing 123a
It is respectively 8mm, 15mm with the axial length of extension 123b.It addition, the inner peripheral surface of cylinder 115 and the sealing as sliding surface
Radius clearance between 123a and extension 123b is 0.005mm.Radius between inner peripheral surface and the non-slip portion 123c of cylinder 115
Clearance is 0.5mm.
On the other hand, it is considered to as shown in Figure 6, both flat with the 1st centrage 141 in axle center representing bearing portion 120
Row, perspective plane parallel with the 2nd centrage 142 in the axle center representing cylinder 115 again.By the 1st centrage the 141 and the 2nd centrage 142
Angulation is set to a1.By that produce because of bearing portion 120 and the diameter clearance of main shaft part 111, rotary shaft 110 relative to axle
The absolute value at the angle of inclination of bearing portion 120 is set to c1 (rad).Cylinder body 114 (cylinder is constituted in the way of a1 and c1 meets formula (1)
115)。
A1=pi/2+c1 ... (1)
Below, to according to the hermetic type compressor constituted with upper type, its action is described.When electrical components 104 is energized,
Rotor 103 makes rotary shaft 110 rotate.By connecting rod 126, the rotation of the eccentric axial portion 112 of the rotation along with rotary shaft 110 is transported
Move and pass to piston 123.
Thus, piston 123 moves back and forth in cylinder 115.By the reciprocating motion of piston 123, by refrigerant gas from tool
The cooling system (not shown) having kind of refrigeration cycle sucks in discharge chambe 116.Refrigerant gas is compressed in discharge chambe 116
After, then be discharged in cooling system.
In the bottom of fuel feeding path 113, the rotation of rotary shaft 110 is utilized to make pumping action produce effect.Hermetic container 101
The lubricating oil 106 of bottom by fuel feeding path 113, be drawn into top, the all-round direction in hermetic container 101 is flatly
Disperse.The lubricating oil 106 dispersed is fed into piston pin 125 and piston 123 etc., carries out the profit of piston pin 125 and piston 123 etc.
Sliding.
Then, the jam of piston is illustrated.
Generally, in the hermetic type compressor of cantilever bearings structure, only with a side shaft of the main shaft part 111 of rotary shaft 110
Prop up and honour compressive load when refrigerant gas is compressed.Therefore, as in figure 2 it is shown, when compression travel compressive load act as
Used time, rotary shaft 110 is tilted with the diameter clearance of bearing portion 120 in main shaft part 111.Therefore, with the axle center C phase of piston 123
The mode angle in the axle center 144 of main shaft part 111 being become to pi/2 (rad) assembles, so valve plate 150 side of piston 123
It is inclined upwardly than horizontal line side by the top being raised up to.
In the present embodiment, it is contemplated that the inclination of this piston 123, valve plate 150 side of the axle center D of cylinder 115 is rising in advance
Rise to being inclined upwardly than horizontal line side by the top and formed.
Therefore, as in figure 2 it is shown, in the case of when compression travel, piston 123 is worked by compressive load, the axle of cylinder 115
Heart D is consistent with the axle center C of piston 123.Thus, the jam of reciprocating piston 123 is alleviated.
In figure 6, the 1st centrage 141 that would indicate that the axle center of bearing portion 120 and the 2nd center in the axle center representing cylinder 115
The intersection point of line 142 is set to O.It addition, by produce with the diameter clearance of main shaft part 111 because of bearing portion 120, rotary shaft 110 phase
Absolute value for the angle of inclination of bearing portion 120 is set to c1.Now, to represent the 1st centrage in the axle center of bearing portion 120
141 meet the mode of formula (1) with angle a1 of the 2nd centrage 142 in the axle center representing cylinder 115 forms cylinder 115.
It is to say, in the present embodiment, using angle a1 shown in formula (1) as the setting of angle in the axle center of cylinder 115
Evaluation.The rotary shaft 110 absolute value c1 relative to the angle of inclination of bearing portion 120 is used angle a1 to be designed to and actual value
Close.Therefore, it is possible to the jam more reliably alleviated between piston 123 and cylinder 115.
On the other hand, during as it is shown on figure 3, piston 123 is worked by captivation when suction stroke, rotary shaft 110 is being led
Axle portion 111 is tilted with the diameter clearance of bearing portion 120.Therefore, with straight relative at bearing portion 120 of the axle center C of piston 123
The angle in the axle center 144 of the main shaft part 111 of the rotary shaft 110 that footpath clearance is tilted becomes the mode of pi/2 (rad) and assembles,
So valve plate 150 side of piston 123 is tilting towards than horizontal line direction on the lower.Accordingly, with respect to considering compression travel
Time the inclination of piston 123 and the axle center D of cylinder 115 that sets, produce skew.
So, in suction stroke, load is attracted piston 123 to be worked, relative to the axle center D of cylinder 115, piston 123
Axle center C tilt in the way of offseting downwards.Now, as it is shown in figure 5, produce because of the axle center deviation angle α of piston 123
, the maximum inclination of the radial direction of sealing 123a represents with the axial length L × sin (α) of sealing 123a.
Generally, in the piston 123 of the hermetic type compressor used in the purposes identical with present embodiment, in order to ensure
Sealing and slip reliability, be formed as sealing 123a by the entire axial length of piston 123.It addition, the radius of sealing 123a
Clearance is minimum in the structural detail of compression element 105, is 0.005mm in the present embodiment.Therefore, during suction stroke
Radius clearance 0.005mm than sealing 123a of the maximum inclination of radial direction of sealing 123a big.Therefore, at piston
The E portion of discharge chambe 116 side of 123 and the F portion of eccentric axial portion 112 side produce jam.
But, in the present embodiment, the sliding part of piston 123 is prolonged by the two sides of sealing 123a and supporting side pressure
Long portion 123b is constituted.Thus, F portion be radius clearance be the non-slip portion 123c of 0.5mm, than the radius clearance of sealing
0.005mm is the biggest.Therefore, piston 123 will not contact at the inner peripheral surface in F portion with cylinder 115.
Further, since length L of sealing 123a is less, even if so near E portion, producing because of axle center deviation angle α
Maximum inclination L × the Sin (α) of the radial direction of raw sealing 123a is also little than radius clearance 0.005mm.
Therefore, even if in the case of attracting load to work in suction stroke, it is also possible to the E portion of suppression piston 123
The generation of jam.
It is to say, the jam between piston 123 and cylinder 115 can be suppressed in compression travel, simultaneously at suction stroke
In also be able to suppress the jam between piston 123 and cylinder 115.
Captivation when being additionally, since this suction stroke is less than compressive load, so the inclination angle of piston 123
Degree when suction stroke than compression travel time little.It addition, the jam of piston 123 and cylinder 115 is also than compression when suction stroke
During stroke little, so the jam significantly reduced between the piston 123 of suction stroke and cylinder 115.
As it has been described above, according to present embodiment, when compression and two strokes of attraction, piston 123 and cylinder can be reduced
The slippage loss of 115 so that it is high efficiency.
As it has been described above, the hermetic type compressor of present embodiment be in hermetic container 101 receive electrical components 104 and by
The hermetic type compressor of the compression element 105 that electrical components 104 drives.Compression element 105 includes: have main shaft part 111 and with
The rotary shaft 110 of the eccentric axial portion 112 of main shaft part 111 one motion；With the main shaft part 111 by axle supporting rotating shaft 110 and
Form the bearing portion 120 of cantilever bearings.It addition, compression element 105 includes: the cylinder 115 that gas is compressed；Can be reciprocally
It is inserted into the piston 123 of the inside of cylinder 115；With the connecting rod 126 linking eccentric axial portion 112 and piston 123.It addition, expression bearing
1st centrage 141 in the axle center in portion 120 and the 2nd centrage 142 angulation a1 and the rotary shaft in the axle center representing cylinder 115
110 meet formula (1) relative to the absolute value c1 at the angle of inclination of bearing portion 120.It addition, the outer peripheral face at piston 123 is provided with
There is gap with the inner peripheral surface of cylinder 115, form the sealing 123a of sliding surface；It is positioned at the rear of sealing 123a, is formed and slide
The extension 123b in face；Be positioned at the rear of sealing 123a, be formed without the non-slip portion 123c of sliding surface.
Thus, when compression and two strokes of attraction, the slippage loss of piston 123 and cylinder 115 can be reduced so that it is high
Efficient activity.
It addition, extension 123b has the radius identical with sealing 123a, and form the sliding surface of supporting side pressure.By
This, it is possible to alleviate the jam of the local of piston, prevent the increase of input, it is achieved high efficiency.
It addition, utilize inverter circuit to drive electrical components 104 with multiple rotating speeds.
Thus, tail off to the fuel delivery of piston when low speed rotation, though the oil of the sliding surface generation at piston
The thickness of film is under thin operating condition, it is also possible to prevent the generation of the jam of piston in cylinder.Even if it addition, at high speed rotating
State under compression ratio is high and in the suction stroke tilting the operating condition becoming big of piston, it is also possible to alleviate piston in cylinder
Jam, it is possible to realize high efficiency.
(embodiment 2)
Fig. 7 is the summary sectional view of the freezer in embodiments of the present invention 2.Wherein, as refrigerating plant, with cold preservation
Illustrate as a example by storehouse.The freezer of Fig. 7 is to load the freezer of the hermetic type compressor of explanation in embodiment 1.
In the figure 7, heat insulating box 180 includes interior case 182, outer container 184 and thermal wall.Interior case 182 is by ABS
The parts of resinite vacuum formings such as (Acrylonitrile, Butadiene, Styrene).Outer container 184 uses precoated steel plate
In metal material.In the space being made up of interior case 182 and outer container 184, inject the insulator 186 of foam filling and formed heat insulation
Wall.In insulator 186, such as, use hard polyurethane foams, phenol formaldehyde foam and styrenic foams etc..As expanded material,
From the viewpoint of preventing greenhouse effect, the Pentamethylene. using hydro carbons can be more preferably.
Heat insulating box 180 is divided into multiple heat insulation marker space, and the structure of revolution door type is formed at top, and pull is formed at bottom
The structure of formula.From top to down, switching chamber 190 and of drawing and pulling type that multiple heat insulation marker spaces are formed as cold room 188, are arranged side by side
The vegetable compartment 194 of ice-making compartment 192 and drawing and pulling type and the refrigerating chamber 196 of drawing and pulling type.Each heat insulation marker space is divided across sealing gasket
It is not provided with insulated door.From top to down, it is cold room revolving door 198, switching chamber sliding door 200, ice-making compartment sliding door 202, vegetables
Dish room sliding door 204 and refrigerating chamber sliding door 206.
It addition, the outer container 184 of heat insulating box 180 has the recess 208 concaving towards end face rear.
Condenser (not shown) that kind of refrigeration cycle by hermetic type compressor 210, is arranged at heat insulating box 180 side etc., make
For decompressor capillary tube 212, carry out the exsiccator (not shown) of moisture removing, vaporizer 216 and suck pipe arrangement 218 connect into
Ring-type.And, hermetic type compressor 210 is the closed-type compressor of explanation in embodiment 1, is resiliently supported in recess
In 208.Vaporizer 216 is at vegetable compartment 194 and the back side of refrigerating chamber 196, and configuration nearby cools down fan 214.
About freezer configured as described above, below, its action, effect are illustrated.
First, the temperature of each heat insulation marker space is set and the type of cooling illustrates.
For stored refrigerated, the temperature of cold room 188, with the temperature that do not freezes as lower limit, is generally set to 1～5 DEG C.
The temperature of switching chamber 190 can be set change by user, it is possible to from freezer temperature territory to cold preservation, vegetable
Change it is set in the temperature field of the regulation in room temperature territory.
Ice-making compartment 192 is independent ice preserving chamber.Ice-making compartment 192 has not shown automatic ice-making plant, automatically makes
Work, ice storage.In order to preserve ice, the temperature of ice-making compartment 192 is in cryogenic temperature territory, but for the preservation of ice, it is also possible to be set in
-18 DEG C～the cryogenic temperature of-10 DEG C higher than cryogenic temperature territory.
Mostly the temperature of vegetable compartment 194 is 2 DEG C～7 DEG C set with the equal or slightly higher temperature of cold room 188.Not
Under the degree freezed, temperature is the lowest, more can the freshness of long term maintenance leafy vegetable.
For freezen protective, generally the temperature of refrigerating chamber 196 is set in-22～-18 DEG C.But, in order to improve freezing
Preservation state, is also set at the low temperature of such as-30～-25 DEG C sometimes.
In order to effectively maintain different temperature to set, thermal wall is utilized to divide each room.But, improve as with low cost
The method of heat-proof quality, it is possible to by insulator 186 foam filling heat insulating box 180 integratedly.By being filled by insulator 186 foaming
Fill out, compared with the situation using heat insulating member as foamed styrene, it is possible to obtain the heat-proof quality of about 2 times, it is possible to because of every
The slimming of plate and expand storage volume etc..
Then, the action to kind of refrigeration cycle illustrates.
According to the temperature of the setting in freezer, utilize from temperature sensor (not shown) and the signal of control substrate,
Start and stop cooling operating.Utilizing the instruction of cooling operating, hermetic type compressor 210 carries out the compressed action specified.Discharge
The refrigerant gas of High Temperature High Pressure heat release and condensation liquefaction in condenser (not shown), be depressurized in capillary tube 212, become
Become the liquid refrigerant of low-temp low-pressure, arrive vaporizer 216.
Utilize the action of cooling fan 214, carry out heat exchange, the cold-producing medium in vaporizer 216 with the air in freezer
Gas evaporation gasifies, and utilizes the cold air of the low temperature after the distribution heat exchanges such as air door (not shown), thus carries out the cooling of each room.
In carrying out above such action, freezer hermetic type compressor 210, such as explanation in embodiment 1
As, the 2nd centrage of the cylinder body 114 the 1st centrage 141 with the axle center representing cylinder 115 to represent the axle center of bearing portion 120
142 cross one another modes are configured with bearing portion 120 and cylinder 115.1st centrage the 141 and the 2nd centrage 142 angulation
A1 (rad) and the rotary shaft 110 that produces because of bearing portion 120 and the diameter clearance of main shaft part 111 are relative to bearing portion 120
The absolute value c1 (rad) at angle of inclination meets formula (1).Piston 123 has between outer peripheral face exists as cylinder 115 inner peripheral surface
Gap also forms the cylindric sealing 123a of sliding surface.It addition, piston 123 has extension 123b, this extension 123b position
In the rear of sealing 123a, there is the radius identical with sealing 123a, and form the sliding surface of supporting side pressure.
Thus, when suction stroke, even if become big feelings with the skew of the axle center in the axle center of piston 123 in the axle center of cylinder 115
Under condition, slide area when piston 123 tilts also diminishes.This is because, piston 123 is at the circle of the sliding surface forming piston 123
The rear of the sealing 123a of cylinder, only has the extension 123b of the sliding surface forming supporting side pressure, on vertical above-below direction
Not there is sliding surface.
As a result of which it is, the jam of the local of piston 123 can be alleviated, reduce slippage loss, improve hermetic type compressor 210
Efficiency.Therefore, it is possible to reduce the consumption electric power of freezer.
As it has been described above, the freezer of present embodiment is the hermetic type compressor using embodiment 1 in kind of refrigeration cycle
Refrigerating plant.Thereby, it is possible to reduce the consumption electric power of refrigerating plant.
Probability is utilized in industry
As it has been described above, the hermetic type compressor of the present invention can improve efficiency by reducing the slippage loss of piston, and
It is not limited to Household Electrical freezing-cooling storeroom, it is possible to be applicable to air conditioner, automatic vending machine and other refrigerating plant etc..
Description of reference numerals
101 hermetic containers
102 stators
103 rotors
104 electrical components
105 compression elements
106 lubricating oil
110 axles
111 main shaft part
112 eccentric axial portion
113 fuel feeding paths
114 cylinder bodies
115 cylinders
116 discharge chambes
120 bearing portions
123 pistons
123a sealing
123b extension
123c non-slip portion
125 piston pins
126 connecting rods
128 big bore ends
129 aperture ends
130 bar portions
141 the 1st centrages
142 the 2nd centrages
144 axle center
150 valve plates
180 heat insulating boxes
Case in 182
184 outer containers
186 insulators
188 cold rooms
190 switching chambers
192 ice-making compartments
194 vegetable compartment
196 refrigerating chambers
198 cold room revolving doors
200 switching chamber sliding doors
202 ice-making compartment sliding doors
204 vegetable compartment sliding doors
206 refrigerating chamber sliding doors
208 recesses
210 hermetic type compressors
212 capillary tubies
214 cooling fans
216 vaporizers
218 suck pipe arrangement
Claims (4)
1. a hermetic type compressor, it is characterised in that:
Electrical components and the compression element driven by described electrical components it is accommodated with in hermetic container,
Described compression element includes:
There is main shaft part and the rotary shaft of the eccentric axial portion with the one motion of described main shaft part；
Support the described main shaft part of described rotary shaft by axle and form the bearing portion of cantilever bearings；
The cylinder that gas is compressed；
Can reciprocally be inserted into the piston of the inside of described cylinder；With
Link the connecting rod of described eccentric axial portion and described piston,
Represent described bearing portion axle center the 1st centrage with represent described cylinder axle center the 2nd centrage angulation a1,
Formula (1) is met relative to the absolute value c1 at the angle of inclination of described bearing portion with described rotary shaft,
A1=pi/2+c1 ... (1)
Outer peripheral face at described piston is provided with
There is gap with the inner peripheral surface of described cylinder, form the sealing of sliding surface；
It is positioned at the rear of described sealing, forms the extension of sliding surface；With
It is positioned at the rear of described sealing, is formed without the non-slip portion of sliding surface.
2. hermetic type compressor as claimed in claim 1, it is characterised in that:
Described extension has the radius identical with described sealing, and forms the described sliding surface of supporting side pressure.
3. hermetic type compressor as claimed in claim 1 or 2, it is characterised in that:
Inverter circuit is utilized to drive described electrical components with multiple rotating speeds.
4. a refrigerating plant, it is characterised in that:
The hermetic type compressor according to any one of claim 1～3 is used in kind of refrigeration cycle.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-033746 | 2014-02-25 | ||
| JP2014033746 | 2014-02-25 | ||
| PCT/JP2015/000651 WO2015129184A1 (en) | 2014-02-25 | 2015-02-13 | Sealed compressor and refrigeration device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106062363A true CN106062363A (en) | 2016-10-26 |
Family
ID=54008522
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580010415.XA Pending CN106062363A (en) | 2014-02-25 | 2015-02-13 | Sealed compressor and refrigeration device |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20170009758A1 (en) |
| JP (1) | JPWO2015129184A1 (en) |
| CN (1) | CN106062363A (en) |
| DE (1) | DE112015000951T5 (en) |
| WO (1) | WO2015129184A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112567133A (en) * | 2018-11-08 | 2021-03-26 | 松下电器产业株式会社 | Refrigerant compressor and refrigeration device using same |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005264740A (en) * | 2004-03-16 | 2005-09-29 | Matsushita Electric Ind Co Ltd | Hermetic compressor |
| CN1806121A (en) * | 2004-07-08 | 2006-07-19 | 松下电器产业株式会社 | Compressor |
| CN101802404A (en) * | 2008-05-12 | 2010-08-11 | 松下电器产业株式会社 | Closed type compressor and freezing apparatus using the same |
| JP2010180740A (en) * | 2009-02-04 | 2010-08-19 | Panasonic Corp | Hermetic compressor and refrigerating unit |
| US20120107148A1 (en) * | 2010-10-27 | 2012-05-03 | Samsung Electronics Co., Ltd. | Hermetic compressor |
| JP2013044255A (en) * | 2011-08-23 | 2013-03-04 | Hitachi Appliances Inc | Closed compressor and refrigerator using the same |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2587246A (en) * | 1949-11-28 | 1952-02-26 | Tresco Inc | Hermetic refrigeration compressor |
| US3419207A (en) * | 1966-09-13 | 1968-12-31 | Hintze Rudolf | Small hermetic compressor |
| BR0116926B1 (en) * | 2001-12-17 | 2010-06-01 | crankshaft on a dual capacity compressor. | |
| JP4760003B2 (en) * | 2004-12-14 | 2011-08-31 | パナソニック株式会社 | Hermetic compressor |
| CN102597518B (en) * | 2009-10-27 | 2016-03-30 | 松下知识产权经营株式会社 | Hermetic type compressor |
-
2015
- 2015-02-13 CN CN201580010415.XA patent/CN106062363A/en active Pending
- 2015-02-13 JP JP2016505029A patent/JPWO2015129184A1/en active Pending
- 2015-02-13 US US15/113,272 patent/US20170009758A1/en not_active Abandoned
- 2015-02-13 DE DE112015000951.5T patent/DE112015000951T5/en not_active Withdrawn
- 2015-02-13 WO PCT/JP2015/000651 patent/WO2015129184A1/en active Application Filing
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005264740A (en) * | 2004-03-16 | 2005-09-29 | Matsushita Electric Ind Co Ltd | Hermetic compressor |
| CN1806121A (en) * | 2004-07-08 | 2006-07-19 | 松下电器产业株式会社 | Compressor |
| CN101802404A (en) * | 2008-05-12 | 2010-08-11 | 松下电器产业株式会社 | Closed type compressor and freezing apparatus using the same |
| JP2010180740A (en) * | 2009-02-04 | 2010-08-19 | Panasonic Corp | Hermetic compressor and refrigerating unit |
| US20120107148A1 (en) * | 2010-10-27 | 2012-05-03 | Samsung Electronics Co., Ltd. | Hermetic compressor |
| JP2013044255A (en) * | 2011-08-23 | 2013-03-04 | Hitachi Appliances Inc | Closed compressor and refrigerator using the same |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112567133A (en) * | 2018-11-08 | 2021-03-26 | 松下电器产业株式会社 | Refrigerant compressor and refrigeration device using same |
| CN112567133B (en) * | 2018-11-08 | 2022-05-31 | 松下电器产业株式会社 | Refrigerant compressor and refrigeration device using same |
Also Published As
| Publication number | Publication date |
|---|---|
| JPWO2015129184A1 (en) | 2017-03-30 |
| WO2015129184A1 (en) | 2015-09-03 |
| US20170009758A1 (en) | 2017-01-12 |
| DE112015000951T5 (en) | 2016-11-03 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| TA01 | Transfer of patent application right | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20170331 Address after: Osaka Japan Applicant after: Matsushita Electric Industrial Co.,Ltd. Address before: Osaka Japan Applicant before: PANASONIC INTELLECTUAL PROPERTY MANAGEMENT Co.,Ltd. |
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| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20161026 |